Electric drive axle for hybrid vehicle

ABSTRACT

An electric drive axle for use in hybrid vehicles has an electric motor driving a compact gearbox. The gearbox includes a planetary reduction unit and a differential assembly. The planetary reduction unit has compound planet gears supported from a planet carrier which mesh with a fixed ring gear and a sun gear driven by the electric motor. The planet carrier drives the differential which transfer motive power to a pair of output shafts adapted for connection to one set of wheels. When used with a conventional engine-based powertrain for the other set of wheels, the electric drive axle establishes a four-wheel drive powertrain for the hybrid vehicle. The electric motor and gearbox are mounted in a common housing assembly to provide a compact drive axle assembly.

FIELD OF THE INVENTION

The present invention relates to hybrid drive systems for motorvehicles. More specifically, the present invention relates to anintegrated electric motor and axle assembly for use in hybrid motorvehicles.

BACKGROUND OF THE INVENTION

Automobile manufacturers are actively working to develop alternativepowertrain systems in an effort to reduce the level of pollutantsexhausted into the air by conventional powertrains equipped withinternal combustion engines. Significant development has been directedto electric vehicles and fuel cell vehicles. Unfortunately, thesealternative powertrain systems suffer from several disadvantages and,for all practical purposes, are still under development. However,several different hybrid electric vehicles (HEV) have recently beenoffered for sale. These hybrid vehicles are equipped with an internalcombustion engine and an electric motor that can be operatedindependently or in combination to drive the vehicle.

There are two types of hybrid vehicles, namely, series hybrid andparallel hybrid. In a series hybrid vehicle, power is delivered to thewheels by the electric motor which draws electrical energy from thebattery. The engine is used in series hybrid vehicles to drive agenerator which supplies power directly to the electric motor or chargesthe battery when the state of charge falls below a predetermined value.In parallel hybrid vehicles, the electric motor and the engine can beoperated independently or in combination pursuant to the runningconditions of the vehicle. Typically, the control strategy for suchparallel hybrid vehicles utilizes a low-load mode where only theelectric motor is used to drive the vehicle, a high-load mode where onlythe engine is used to drive the vehicle, and an intermediate assist modewhere the engine and electric motor are both used to drive the vehicle.Regardless of the type of hybrid drive system used, hybrid vehicles arehighly modified versions of conventional vehicles that are expensive dueto the componentry, required control systems, and specialized packagingrequirements.

Hybrid powertrains have also been adapted for use in four-wheel drivevehicles and typically utilize the above-noted parallel hybridpowertrain to drive the primary wheels and a second electric motor todrive the secondary wheels. Obviously, such a four-wheel drive system isextremely expensive and difficult to package. Thus, a need exists todevelop hybrid powertrains for use in four-wheel drive vehicles thatutilize many conventional powertain components so as to minimizespecialized packaging and reduce cost.

SUMMARY OF THE INVENTION

It is an object of the present invention to provide a hybrid powertrainof drive system for a four-wheel drive vehicle.

It is another object of the present invention to provide an integratedgearbox and electric motor assembly for use as an electric drive motoraxle in a hybrid vehicle.

As a related object, the hybrid drive system of the present inventionutilizes an internal combustion engine as a first drive source to supplymotive power to a first set of wheels and further uses the electricdrive motor axle as a second drive source to supply motive power to asecond set of wheels. A control system functions to control operation ofthe first and second drive sources either independently or incombination was dictated by the current vehicle operating conditions.

These and other objects are provided by an electric motor drive axlehaving an electric motor and a gearbox packaged within a common housingassembly. The gearbox includes a differential assembly interconnecting apair of axleshafts, and a planetary reduction unit having an inputmember driven by the electric motor and an output member driving thedifferential assembly. The planetary reduction unit includes a sun geardriven by the motor, a ring gear fixed to the housing assembly, a planetcarrier fixed to an input member of differential assembly, and acompound planet gear having a first gear segment meshed with the sungear and a second gear segment meshed with the ring gear.

Further areas of applicability of the present invention will becomeapparent from the detailed description provided hereinafter. However, itshould be understood that the detailed description and specificexamples, while indicating preferred embodiments of the presentinvention, are intended for purposes of illustration only since variouschanges and modifications within the fair scope of this particularinvention will become apparent to those skilled in the art.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic view showing a hybrid powertrain for a four-wheeldrive vehicle in accordance with the present invention;

FIG. 2 is a schematic view of an alternative arrangement for the hybridpowertrain of the present invention;

FIG. 3 is a sectional view of an electric drive motor axle associatedwith the hybrid powertrains of FIGS. 1 and 2;

FIG. 4 is an enlarged portion of FIG. 3 showing the componentsassociated with the gearbox of the electric drive motor axle in greaterdetail;

FIG. 5 is a sectional view of an alternative embodiment of the gearboxthat is adapted for use in the electric drive motor axle of the presentinvention;

FIG. 6 is a sectional view of a further alternative embodiment of thegearbox for use in the electric drive motor axle of the presentinvention;

FIG. 7 is a partial sectional view of a planetary-type differentialadapted for use with the gearboxes shown in FIGS. 4 through 6; and

FIG. 8 is a schematic diagram of an exemplary control system associatedwith the hybrid powertrains of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

The present invention is related to an integrated gearbox and electricmotor assembly, hereinafter referred to as electric drive motor axle,which functions as an electrically-controlled transaxle in a hybridmotor vehicle for delivering motive power (i.e., drive torque) to a pairof ground-engaging wheels. The compact arrangement of the electric motorand gearbox in a common housing permits the use of the electric drivemotor axle in substitution for a conventional axle assembly. As such,conventional rear-wheel drive and front-wheel drive powertrains can beused in combination with the electric drive motor axle so as toestablish a hybrid drive system for a four-wheel drive vehicle.Accordingly, various features and functional characteristics of theelectric drive motor axle will be set forth below in a manner permittingthose skilled in relevant arts to fully comprehend and appreciate thesignificant advantages the present invention provides, particularly whenused in four-wheel drive hybrid vehicles.

Referring to FIG. 1, a four-wheel drive powertrain for a hybrid electricvehicle 10 is shown to include a first powered driveline 12 and a secondpowered driveline 14. First powered driveline 12 includes an internalcombustion engine 16, a transmission 18, a drive shaft 20, and an axleassembly 22 connecting a pair of wheels 24. Engine power is delivered toa differential unit 26 associated with axle assembly 22 throughtransmission 18 and drive shaft 20. The drive torque delivered todifferential unit 26 is transferred through axleshafts 28 and 30 towheels 24. Second powered driveline 14 includes an electric drive motoraxle (EDMA) 32 which drives a second pair of wheels 34 throughaxleshafts 36 and 40.

In the particular layout shown in FIG. 1, first powered driveline 12delivers power to rear wheels 24 while second powered driveline 14delivers power to front wheels 34. Obviously, those skilled in the artwould understand that the opposite powertrain arrangement can beutilized such that EDMA 32 supplies power to the rear wheels. To betterillustrate this arrangment, FIG. 2 shows EDMA 32 supplying power to rearwheels 24 through axleshafts 28 and 30 while engine power is supplied tofront wheels 34 through a transaxle 18A and axleshafts 36 and 40.Regardless of the particular arrangement, hybrid vehicle 10 includes twodistinct powered drivelines capable of both independent and combinedoperation to drive the vehicle.

Referring now to FIGS. 3 and 4, a first preferred embodiment of EDMA 32will be described in detail. EDMA 32 includes a multi-section housingassembly 50 defining a motor chamber 52 and a gearbox chamber 54separated by a radial support wall 56. An electric variable speed motorassembly 58 is located within motor chamber 52 and includes a woundstator 60 secured to housing assembly 50 and an elongated tubular rotorshaft 62. Rotor shaft 62 is supported at its opposite ends by bearingassemblies 64 for rotation relative to housing assembly 50. Motorassembly 58 also includes a rotor assembly 66 fixed for rotation withrotor shaft 62.

EDMA 32 further includes a gearbox 68 located within gearbox chamber 54and which is comprised of a planetary reduction unit 70 and a beveldifferential 72. Planetary reduction unit 70 includes a sun gear 74, aring gear 76, and a plurality of compound planet gears 78 rotatablysupported by bearings 80 on pins 82 mounted to a planet carrier 84. Sungear 74 can be integrally formed at one end of rotor shaft 62 (as shownin upper-half of FIG. 3) or, in the alternative, can be a tubular unitthat is fixedly secured to rotor shaft 62 (as shown in lower-half ofFIG. 3). As best seen from FIG. 4, sun gear 74 is fixed via a splineconnection 86 for rotation with rotor shaft 62 while ring gear 76 isfixed to housing assembly 50. Snap rings 88 and 90 are provided torestrain axial movement of sun gear 74 and ring gear 76, respectively.Each compound planet gear 78 includes a first gear segment 92 that ismeshed with sun gear 74 and a second gear segment 94 that is meshed withring gear 76. First and second gear segments 92 and 94 can be integrallyformed or, in the alternative, can be defined by separate gears whichare rigidly fixed together (i.e., welded) for common rotation. Planetcarrier 84 is shown to include a first ring section 96 and a second ringsection 98 integrally connected at a plurality of circumferentiallocations by a lug section 100. First ring section 96 is shown to besupported for rotation by a bearing assembly 102.

With continued reference to FIG. 4, bevel differential 72 is shown toinclude a bell-shaped casing 104 having a radial ring segment 106secured via bolts 107 to second ring section 98 of planet carrier 84.Bevel differential 72 further includes a first side gear 108 fixed via aspline connection 110 to a first output shaft 112, a second side gear114 fixed via a splined connection 116 to a second output shaft 118, andat least one pair of pinions 120 meshed with side gears 108 and 114.Pinions 120 are rotatably supported on a pinion shaft 122 having itsopposite ends located in polar apertures 124 formed in casing 104. Aretainer pin 126 mounted in a transverse aperture 128 formed in casing104 passes through pinion shaft 122 so as to non-rotatably mount pinionshaft 122 to casing 104. Casing 104 is also configured to define acircumferential bearing surface for supporting an axial extension offirst side gear 108. Likewise, second ring section 98 of planet carrier84 defines a circumferential bearing surface for supporting an axialextension of second side gear 114. In addition, snap rings 130 and 132axially restrain side gears 108 and 114 relative to the respectiveoutput shafts 112 and 118. A bearing assembly 134 is shown to rotatablysupport casing 104 from housing assembly 50.

In accordance with a preferred use of EDMA 32, output shafts 112 and 118are adapted to be connected to corresponding ones of front axleshafts 36and 40 for the hybrid powertrain arrangement shown in FIG. 1 or,alternatively, to corresponding ones of rear axleshafts 28 and 30 forthe powertrain arrangement shown in FIG. 2. In this manner, EDMA 32functions as an electrically-powered secondary axle assembly which canbe controlled independently, or in combination with, the engine-basepowertrain. To provide a compact arrangement, second output shaft 118 isshown to extend through tubular rotor shaft 62. Bearings 136 and 138support output shafts 112 and 118, respectively, for rotation relativeto housing assembly 50. Additionally, resilient end seals 140 and 142are provided. It is contemplated that a lube pump 139 could be providedto circulate lubricant with gearbox chamber 54. Lube pump 139 could beelectric or shaft driven as required.

In operation, rotation of rotor shaft 62 via actuation of electric motorassembly 58 causes concurrent rotation of sun gear 74. Since ring gear76 is held stationary, rotation of sun gear 74 causes compound planetgears 78 to rotate and drive planet carrier 84 at a reduced speed.Obviously, the speed reduction ratio is established by the specificgeometries of the meshing gears, but is preferred to be in the range of10.0:1 to 15.0:1 for such hybrid motor vehicle applications. Sinceplanet carrier 84 acts as the driven output of planetary reduction unit70, it drives casing 104 of bevel differential 72 at a common rotaryspeed. Power is then transferred through pinions 120 to side gears 108and 114 and ultimately to output shafts 112 and 118. Variable speedcontrol of motor assembly 58 permits the torque delivered to the wheelsto be variably controlled.

Referring now to FIG. 5, a slightly modified gearbox 68A is shownlocated within gearbox chamber 54 of housing assembly 50. Specifically,differential casing 104A is now shown to be integrally formed withsecond ring section 98 of planet carrier 84 and an end cap 105 issecured via bolts 107 to differential casing 104A. As such, first sidegear 108 is now supported by a circumferential bearing surface providedby end cap 105 and bearing assembly 134 supports end cap 105 fromhousing assembly 50.

Referring to FIG. 6, another modified gearbox 98B is shown whereinplanetary reduction unit 70B has the gear segments 92B and 94B ofcompound planet gears 78B reversed relative to that shown in FIGS. 4 and5. This arrangement requires use of a slightly longer sun gear 74B. Inaddition, differential casing 104B is shown to be integrally formed withplanet carrier 84 so as to eliminate bolts 107. Assembly windows (notshown) would be formed in differential casing 104B to permit assembly ofpinions 120 and side gears 108 and 114 therein. A yoke 146 is shownintegrally formed at one end of first output shaft 112 in place of theslip yoke splines shown in FIGS. 3 through 5.

Referring now to FIG. 7, an alternative type of differential unit 150 isshown which can be substituted for the bevel-type differentialpreviously described. In particular, differential unit 150 is aplanetary gearset having an annulus gear 152 driven by second ringsegment 98 of planet carrier 84, an output sun gear 154 fixed to firstoutput shaft 112, and an output carrier 156 fixed via a splinedconnection 158 to second output shaft 118. Differential unit 150 alsoincludes a set of first pinions 160 that are meshed with annulus gear152 and a set of second pinions 162 (shown in phantom) that are meshedwith output sun gear 154 and first pinions 160. Output carrier 156includes an outer ring segment 164 connected to an inner ring segment166 between which pinions 160 and 162 are rotatably supported.Specifically, pins 168 support first pinions 160 while similar pins (notshown) rotatably support second pinions 162. First pinions 160 andsecond pinions 162 are circumferentially arranged in a plurality ofmeshed pairs to transfer drive torque and facilitate speeddifferentiation between output carrier 156 and output sun gear 154. Abearing 170 is shown supporting second ring segment 98 of planet carrier84 from second output shaft 118. Thus, differential unit 150 exemplifiesa planetary-type gearset that can be used in place of bevel-typegearsets, it being understood that other arrangements known for use as avehicular differential could also be used.

As noted, the hybrid powertrain system of the present invention includestwo drive power sources, namely engine 16 and motor assembly 58 of EDMA32. Power from engine 16 is transmitted to transmission 18 (or transaxle18A) which can be of any known type (i.e., automatic, manual, automatedmanual, CVT, etc.) having a forward-reverse mechanism and a gearshiftmechanism. Motor assembly 58 of EDMA 32 is connected to a battery 200and can be selectively shifted into any of a DRIVE state, a CHARGINGstate, and a NO-LOAD state by an electronic control system 202. In theDRIVE state, EDMA 32 functions as a motor-driven gearbox that is drivenby electrical energy drawn from battery 200. In the CHARGING state, EDMA32 functions as an electric generator for storing electric energy inbattery 200. In the NO-LOAD state, motor assembly 58 is off and rotorshaft 62 is permitted to rotate freely relative to stator 60.

Control system 202 is provided for controlling operation of the hybridpowertrains shown in FIGS. 1 and 2. Referring to FIG. 8, control system202 includes a controller 204 adapted to receive input signals fromvarious sensors and input devices cumulatively identified in FIGS. 1 and2 as vehicle sensors 206. Controller 204 is schematically shown in blockformat to be representative of an arrangement having an engine controlsection, a motor control sections, and a traction control section.Controller 204 is principally comprised of a microcomputer having acentral processing unit (CPU), random-access memory (RAM), read-onlymemory (ROM), and an input-output actuator interface. Controller 204performs data processing operations to execute various control routinesaccording to control programs and/or maps stored in the ROM. Controller204 receives data from an ignition switch 208, a gearshift lever switch210, an accelerator position sensor 212, a brake status switch 214, abattery temperature sensor 216, a battery SOC (state of charge) sensor218, and a throttle position sensor 220. In addition, other inputsinclude an engine speed sensor 222, a motor speed sensor 226, and adriveshaft speed sensor 228. Ignition switch 208 is closed when thevehicle key is turned on. Assuming transmission 18 is of an automatictype, then “P”, “N”, “R”, and “D” switches in gearshift selector switch210 are closed when the gearshift mechanism is located in its Park (P),Neutral (N), Reverse (R) and Drive (D) positions, respectively.Accelerator position sensor 212 senses the depression angle of anaccelerator pedal. Brake status switch 214 is turned on when the brakepedal is depressed. Battery temperature sensor 216 senses thetemperature of battery 200. Battery SOC sensor 218 senses the chargelevel of battery 200. Throttle position sensor 220 senses the degree ofopening of the engine throttle valve. Engine speed sensor 222 senses aparameter indicative of the rotary speed of the drive shaft of engine16. Motor speed sensor 226 senses a parameter indicative of the rotaryspeed of rotor 62 of motor assembly 58. Shaft speed sensor 228 sensesthe rotary speed of propshaft 20 and can further be used as anindication of vehicle speed.

Based on the operating information inputted to controller 204, a mode ofoperation of the hybrid powertrain is selected and controller 204 sendselectric control signals to various power-operated control devices.Specifically, controller 204 monitors and continuously controlsactuation of motor assembly 58 of EDMA 32 and various engine managementsystems for controlling the speed and torque generated by engine 16.These engine management systems include a fuel delivery system 230, anignition system 232, and a valve timing system 234. A low voltagebattery 236 may serve as the power supply for controller 204.

There are four modes of operation for vehicle 10, namely: (a) anelectric mode; (b) a hybrid; (c) an engine mode; and (d) a regenerativemode. In the electric mode, only motor assembly 58 provides motive powerto vehicle 10. In the hybrid mode, both engine 16 and motor assembly 58provide motive power to vehicle 10. In the engine mode, only engine 16provides motive power to vehicle 10. In the regenerative mode, a portionof the engine power is absorbed by motor assembly 58 to charge battery200. The transition from one mode to the next is smooth and transparentto the vehicle operator since controller 204 selects the mostappropriate mode depending on various vehicle operating conditionsincluding vehicle speed, accelerator demand and battery charge status.

In the electric mode, motor assembly 58 is shifted into its DRIVE statesuch that motive power is generated by EDMA 32. When shifting from theelectric mode into the hybrid mode, engine 16 is started and providesmotive power in conjunction with EDMA 32 to establish four-wheel driveoperation. When the vehicle's operating conditions warrant operation inthe engine only mode, motor assembly 58 is shifted into one of itsCHARGING or NO-LOAD states. Thus, a four-wheel drive mode of operationis established when both powered drivelines are actuated and controlled.The traction control section of controller 204 is operable to controlslip conditions between the front and rear wheels.

Preferred embodiments of the invention has been disclosed to providethose skilled in the art an understanding of the best mode currentlycontemplated for the operation and construction of the hybrid drivesystems. The invention being thus described, it will be obvious thatvarious modifications can be made without departing from the true spiritand scope of the invention, and all such modifications as would beconsidered by those skilled in the art are intended to be includedwithin the scope of the following claims.

What is claimed is:
 1. A drive axle for a motor vehicle, comprising: ahousing defining first and second chambers; an electric motor disposedin said first chamber and having a rotor shaft extending into saidsecond chamber; and a gearbox disposed in said second chamber andoperably coupling said rotor shaft to first and second output shafts,said gearbox including a planetary reduction gearset having a ring gearfixed to said housing, a sun gear driven by said rotor shaft, a planetcarrier, and compound planet gears rotatably supported by said planetcarrier and having a first gear segment meshed with said sun gear and asecond gear segment meshed with said ring gear, said gearbox furtherincluding a differential assembly having an input member driven by saidplanet carrier, a first output member driving said first output shaft,and a second output member driving said second output shaft.
 2. Thedrive axle of claim 1 wherein said rotor shaft is tubular and isrotatably supported on said second output shaft.
 3. The drive axle ofclaim 1 wherein said differential assembly is a bevel gearset having adifferential casing fixed for rotation with said planet carrier, a firstside gear fixed for rotation with said first output shaft, a second sidegear fixed for rotation with said second output shaft, and pinionsrotatably supported by said casing and meshed with said first and secondside gears.
 4. The drive axle of claim 3 wherein said planet carrierincludes a first ring offset from and interconnected to a second ringwith said compound planet gears rotatably supported on pins extendingbetween said first and second rings.
 5. The drive axle of claim 4wherein said differential casing includes a radial plate segment fixedlysecured to said second ring of said planet carrier.
 6. The drive axle ofclaim 4 wherein said second ring of said planet carrier is integral withsaid differential case.
 7. The drive axle of claim 1 wherein saiddifferential assembly is a planetary gearset having a second ring gearfixed for rotation with said planet carrier, an output sun gear fixedfor rotation with said first output shaft, an output carrier fixed forrotation with said second output shaft, a first pinion rotatablysupported by said output carrier and meshed with said second ring gear,and a second pinion rotatably supported by said output carrier andmeshed with said first pinion and said output sun gear.
 8. The driveaxle of claim 1 wherein said first and second output shafts are adaptedfor connection to a pair of first wheels to deliver drive torque theretoin response to actuation of said electric motor.
 9. The drive axle ofclaim 8 wherein said first wheels are front wheels of the motor vehicle.10. The drive axle of claim 9 wherein the motor vehicle has rear wheelsdriven by power from an engine.
 11. The drive axle of claim 8 whereinsaid first wheels are rear wheels of the motor vehicle.
 12. The driveaxle of claim 11 wherein the motor vehicle has front wheels driven bypower from an engine.
 13. An electrically-powered drive axle for drivinga pair of wheels in a motor vehicle, comprising: a housing; first andsecond output shafts rotatably supported by said housing and adapted forconnection to the pair of wheels; an electric motor assembly disposed insaid housing and having a rotor shaft; and a gearbox disposed in saidhousing and including a planetary reduction gearset and a beveldifferential, said planetary reduction gearset having a sun gear drivenby said rotor shaft, a ring gear non-rotatably secured to said housing,a planet carrier, and a plurality of compound planet gears rotatablysupported by said planet carrier and having a first gear segment meshedwith said sun gear and a second gear segment meshed with said ring gear,said bevel differential having a casing driven by said planet carrier, afirst side gear fixed for rotation with said first output shaft, asecond side gear fixed for rotation with said second output shaft, andpinions rotatably supported by said casing and meshed with said firstand second side gears.
 14. The drive axle of claim 13 wherein said rotorshaft is tubular and is rotatably supported on said second output shaft.15. The drive axle of claim 13 wherein said planet carrier includes afirst ring offset from and interconnected to a second ring with saidcompound planet gears rotatably supported on pins extending between saidfirst and second rings.
 16. The drive axle of claim 15 wherein saiddifferential casing includes a radial plate segment fixedly secured tosaid second ring of said planet carrier.
 17. The drive axle of claim 15wherein said second ring of said planet carrier is integral with saiddifferential case.
 18. The drive axle of claim 13 further comprising:vehicle sensors for detecting operating characteristics of the motorvehicle and generating sensor signals; and a controller for generatingelectrical control signals in response to said sensor signals, saidcontrol signals being delivered to said motor assembly for controllingthe rotary speed of said rotor shaft.
 19. An electrically-powered driveaxle for driving a pair of wheels in a motor vehicle, comprising: ahousing; first and second output shafts rotatably supported by saidhousing and adapted for connection to the pair of wheels; an electricmotor assembly disposed in said housing and having a rotor shaft; and agearbox disposed in said housing and having a first sun gear driven bysaid rotor shaft, a first ring gear fixed to said housing, a firstcarrier, and compound planet gears rotatably supported by said firstcarrier and having a first gear segment meshed with said first sun gearand a second segment meshed with said first ring gear, said gearbox alsoincluding a second ring gear driven by said first carrier, a second sungear fixed for rotation with said first output shaft, a second carrierfixed for rotation with said second output shaft, a set of first pinionsrotatably supported by said second carrier and meshed with said secondring gear, and a set of second pinions rotatably supported by saidsecond carrier and meshed with said second sun gear and said firstpinions.
 20. The drive axle of claim 19 wherein said rotor shaft istubular and is rotatably supported on said second output shaft.
 21. Thedrive axle of claim 19 further comprising: vehicle sensors for detectingoperating characteristics of the motor vehicle and generating sensorsignals; and a controller for generating electrical control signals inresponse to said sensor signals, said control signals being delivered tosaid motor assembly for controlling the rotary speed of said rotorshaft.
 22. A hybrid motor vehicle, comprising: a first powered drivelineincluding an engine operable for driving a first pair of wheels; and asecond powered driveline including a drive axle operable for driving asecond pair of wheels, said drive axle including a housing, an electricmotor located in said housing and having a rotor shaft, and a gearboxlocated in said housing and having a reduction gearset and adifferential, said reduction gearset having a sun gear driven by saidrotor shaft, a ring gear fixed to said housing, a planet carrier, andcompound planet gears supported by said planet carrier and having afirst gear segment meshed with said sun gear and a second gear segmentmeshed with said ring gear, said differential having an input memberdriven by said planet carrier and first and second output membersdriving said second pair of wheels.
 23. The hybrid motor vehicle ofclaim 22 wherein said drive axle further includes a first output shaftcoupled to said first output member and a second output shaft coupled tosaid second output member, and wherein said rotor shaft is tubular androtatably supported on said second output shaft.
 24. The hybrid motorvehicle of claim 23 wherein said differential is a bevel gearset havinga casing fixed for rotation with said planet carrier, a first side gearfixed for rotation with said first output shaft, a second side gearfixed for rotation with said second output shaft, and pinions rotatablysupported by said casing and meshed with said first and second sidegears.
 25. The hybrid motor vehicle of claim 23 wherein saiddifferential is a planetary gearset having a second ring gear fixed forrotation with said planet carrier, an output sun gear fixed for rotationwith said first output shaft, an output carrier fixed for rotation withsaid second output shaft, a first pinion rotatably supported by saidoutput carrier and meshed with said second ring gear, and a secondpinion supported by said output carrier and meshed with said firstpinion and said output sun gear.
 26. The hybrid motor vehicle of claim22 further comprising: vehicle sensors for detecting operatingcharacteristics of the motor vehicle and generating sensor signals; anda controller for generating electrical control signals in response tosaid sensor signals, said control signals being delivered to said motorassembly for controlling the rotary speed of said rotor shaft.